WO2013149793A1

WO2013149793A1 - Actuating device for a clutch

Info

Publication number: WO2013149793A1
Application number: PCT/EP2013/055031
Authority: WO
Inventors: Thomas Eckenfels; Steffen Huber; Gerold Steinel
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2012-04-03
Filing date: 2013-03-12
Publication date: 2013-10-10
Also published as: DE102013204280A1; DE112013001931A5

Abstract

The invention relates to an actuating device for a clutch, comprising a stator device, a rotor device which is rotatable relative to the stator device, and a slide which can be moved relative to the rotor device in the axial direction in a restricted manner. A rolling element threaded drive with at least three threads and with a rolling element housing comprising rolling elements is provided between the rotor device and the slide, said rolling element housing having a track switching region which is designed such that rolling elements upstream of the track switching region in the circumferential direction run between a first thread and a second thread, and rolling elements downstream of the track switching region in the circumferential direction run between the second thread and a third thread. At least one tilt torque support device is provided for supporting a tilt torque acting on the slide.

Description

Actuator for a clutch

The present invention relates to an actuating device for a clutch, in particular for a motor vehicle clutch.

From the older but not previously published DE 10 201 1 102 222.1, an actuating device for a clutch with a stator device, a rotor device rotatable with respect to the stator device and a slide device which is displaceable in the axial direction with respect to the rotor device is known. Between the rotor device and the carriage device, a Wälzkörpergewindetrieb is provided with a plurality of turns and a Wälzkörperumlauf with rolling elements. The Wälzkörperumlauf has a track change region formed in such a way that rolling elements in the circumferential direction before the lane change region between a first and a second turn run, and rolling elements in the circumferential direction after the lane change region between the second and a third turn run.

Since the actuated by the actuator coupling is not formed tilt-rigid or has no defined leadership, there is a possibility that the carriage means which acts directly or indirectly on the clutch is tilted by the clutch. This can lead to increased wear of the Wälzkörperumlaufs and the rolling elements.

It is an object of the present invention to provide an actuating device for a clutch, in which the wear of the components involved can be reduced.

This object is achieved by an actuating device for a clutch according to claim 1 with a stator, a rotor device rotatable relative to the stator and a limited relative to the rotor device in the axial direction displaceable carriage means, wherein between the rotor means and the carriage means a Wälzkörpergewindetrieb with at least three turns and a Wälzkörperumlauf is provided with rolling elements, wherein the Wälzkörperumlauf has a track change region formed in such a way that rolling elements run in the circumferential direction before the lane change area between a first and a second turn, and Wälzkörper run body in the circumferential direction after the lane change area between the second and a third turn.

Since at least one Kippmomentabstützungseinrichtung for supporting a on the

Sliding device acting tilting moment is provided, the wear of the components involved, in particular the Wälzkörperumlaufs and the rolling elements can be reduced.

Preferred embodiments of the present invention are in the dependent

Claims set forth.

In particular, the actuating device for the clutch of a motor vehicle

educated. The clutch is in particular a friction clutch, as provided between the internal combustion engine and the transmission of a motor vehicle for the gear change. The coupling may be formed on the one hand as a single clutch, but may also be designed as a multiple clutch, in particular as a double clutch. In a double clutch preferably two actuators of the aforementioned type are provided.

Furthermore, the coupling can be designed both as a dry clutch and as a wet clutch. The clutch may be on the one hand to an engaged in the non-actuated state, that is normal-engaged clutch, or on the other hand, a disengaged in the non-actuated state, that is normal-disengaged clutch. In a normally-engaged clutch, the lever element on which the actuator acts, is usually designed as a plate spring, while in a normally-disengaged clutch, the lever element on which the actuator acts, is usually designed as a lever spring. Further, the clutch on the one hand as a depressed clutch, that is, as a clutch in which the actuating device exerts a pressing force on the lever member, or on the other hand as a drawn clutch, that is, as a clutch, in which the actuating device exerts a pulling force on the lever member is formed be.

The stator device and the stator device preferably form with respect to the stator device

rotatable rotor means an electric motor. The electric motor is preferably designed as a three-phase motor, are provided on the stator side of the magnets, more precisely permanent magnets, rotorsei- tig and alternately energizable turns. According to one preferred embodiment, the electric motor is designed as an external rotor, that is, in its interior on the stator, which is surrounded by the annular rotatable rotor means. However, the electric motor can also be designed as an internal rotor.

The actuating device can be supplied with current via a power supply and is preferably mounted in the drive train of the motor vehicle such that it must be energized exclusively for engagement and disengagement of the clutch. By the Wälzkörpergewindetrieb, which is arranged in the path of action between the rotor means and the carriage means, a rotational movement of the rotor means is converted into a translational movement of the carriage means. The Wälzkörpergewindetrieb is preferably self-locking. About a release bearing, which is for example designed as angular contact ball bearings, but can also be designed as a tapered roller bearing, needle bearing or sliding bearing, the carriage means can act directly or indirectly on the lever member of the clutch.

For example, the stator can be non-rotatably formed with a support portion, in particular with a housing support, so that the power supply of the stator by means of cables and without rotary feedthrough or inductive coupling is possible. In the radial direction within the stator, the input shaft of the clutch or the output shaft of the internal combustion engine extends. The input shaft is rotatably mounted with respect to the stator device or the carrier section.

However, it is also possible that the stator is rotatably mounted on the input shaft of the clutch, that is, rotates with the speed of the internal combustion engine. In this case, a rotary feedthrough or an inductive coupling for energizing the actuator is required. The energization of the actuator in one direction produces an increased rotational speed of the rotor means compared to the input speed of the driveline, thereby disengaging the clutch. The energization of the actuator in the other direction produces a reduced rotational speed of the rotor device compared to the input rotational speed of the drive train, whereby the clutch is engaged. Therefore, the disengagement operation of the clutch can be initiated via an acceleration of the rotor device, while the engagement of the clutch is initiated via a deceleration of the rotor device. Likewise, it is also possible that the disengaging operation of the clutch is initiated by a braking of the rotor device, while the engagement of the clutch is initiated by accelerating the rotor device. According to a preferred embodiment, the Wälzkörpergewindetrieb on an outer sleeve, in which a form of spring is inserted, which has a plurality of turns. The form spring is formed in particular from a helically wound spring wire, wherein in a preferred embodiment, the coiled spring wire is contoured, that is, provided in the axial direction on both sides with a contact contour, which is separated by an intervening comb. The adjacent contact contours of two successive turns of the form spring form part of the surface geometry of the rolling element, so that the respective rolling element can be guided in the axial direction in a direction extending in the circumferential direction track between two adjacent turns of the form spring.

The outer sleeve is closed by a lid for supporting the shaped spring, which is screwed to the outer sleeve by a plurality of circumferentially distributed arranged screws. Between the cover and the outer sleeve, a shim is preferably provided. Shims are available in different thicknesses to ensure the operation of the actuator on the one hand, the widest possible backlash of Wälzkörpergewin- detriebs in the axial direction and on the other hand, the ease of movement and in particular the freedom from jamming of Wälzkörpergewindetriebs. By means of the appropriate shim is therefore the axial length of the space in which the helical shape spring is arranged to adjust exactly when assembling the actuator.

According to a preferred embodiment, a first Kippmomentabstützeinrichtung is disposed in the region of a first end of the carriage device. A second Kippmomentabstützeinrichtung is in the range of a second, the first end in the axial direction opposite end of the carriage means arranged. In this way, it is possible, when viewing the actuator from the side of a tilting moment acting on the carriage means support both clockwise and counterclockwise.

It is advantageous if two tilting moment supporting devices lying opposite one another in the axial direction delimit a grease space in which the rolling element circulation, and preferably the form spring, which has at least the first, second and third turns is / are arranged. It is advantageous if the Kippmomentabstützeinrichtungen simultaneously take over the function of seals, of which one is provided on the outer sleeve side and the other cover side. The space between the two seals is preferably with grease filled to minimize the friction of the Wälzkörpergewindetriebs and to prevent jamming of the rolling elements.

Preferably, the Kippmomentabstützeinrichtung has at least one ring and at least one inner sleeve. The ring is in slidable or rollable engagement with the inner sleeve. In particular, it is advantageous if both Kippmomentabstützeinrichtungen each have a ring and one inner sleeve.

It is advantageous if the ring is attached directly or indirectly to the carriage device, and if the inner sleeve is attached directly or indirectly to the stator device. In this case, it is advantageous if the ring and the inner sleeve do not undergo rotation relative to one another, since the slide device and the stator device also advantageously undergo no rotation relative to one another during operation of the actuating device and in particular are designed to be rotationally fixed relative to one another. Preferably, the ring is attached to the outer sleeve or on the lid of the carriage device. In particular, it is advantageous if the ring is pressed into the outer sleeve or the lid of the carriage device.

According to a further preferred embodiment, the inner sleeve has a smaller diameter than the outer sleeve of the carriage device. Preferably, the inner sleeve extends in the axial direction at least partially within the outer sleeve of the carriage device. In particular, it is advantageous if both inner sleeves extend in the axial direction at least partially within the outer sleeve of the carriage device.

According to a further preferred embodiment, the ring has a block-shaped cross-section. Preferably, the ring is formed of a rigid and / or pressure-stable material.

It is advantageous if the ring is formed from a plastic or a sintered material. In particular, it is advantageous if polytetrafluoroethylene (PTFE) is used as the plastic. If the ring is formed of a sintered material, it is particularly advantageous if a lubricant is incorporated in the sintered ring.

According to another preferred embodiment, the ring has a coating with reduced friction properties, preferably of polytetrafluoroethylene (PTFE). According to a further preferred embodiment, the ring has a rolling bearing. This roller bearing advantageously allows only a displacement of the ring to the inner sleeve in the axial direction, since in operation of the actuator of the ring and the inner sleeve advantageously no rotation to each other, as well as in particular during operation of the actuator, the carriage device and the stator in an advantageous manner no twist to each other. Preferably, the carriage device and the stator are rotatably formed to each other.

The Wälzkörperpernlauf of Wälzkörpergewindetriebs filled with rolling elements is preferably formed integrally with the rotor device, more precisely in one piece with a yoke of the rotor device. The yoke of the rotor device is rotatably supported via a support bearing, in particular a radial bearing, indirectly or directly on the stator.

In addition to the lane change region, the rolling element circulation has at least one support region, which is arranged in circumferential direction before the lane change region and after the lane change region. In the lane change region, during operation of the actuating device, that is, upon rotation of the rotor device, the revolving rolling elements are displaced from a track of the shaped spring into an adjacent track of the shaped spring. More specifically, the rolling elements are arranged in Umfangsnchtung before the lane change area in the support area in the track between a first and a second turn of the form spring, while the rolling elements are arranged in Umfangsnchtung after the lane change area in the support area in the track between the second and a third turn of the form spring ,

The support region of the rolling element circulation is formed substantially helically. The pitch of the helical support portion corresponds to the track between the first and second turns of the form spring in which the rollers run. Similarly, the pitch of the helical support portion corresponds to the track between the second and third turns of the forming spring in which the rolling elements travel.

In a preferred embodiment, the Wälzkörperumlauf is arranged in the outer circumference of the rotor device in an external rotor designed as an electric motor, while accordingly the form spring, between whose turns the rolling elements run, arranged radially outside and formed as an inner contoured shape spring, both the comb and the investment contours for the rolling elements point radially inwards. However, it is also possible, for example, in the formation of the electric motor as Internal rotor to provide the Wälzkörperumlauf in the inner circumference of a rotor device, and accordingly to arrange the form spring radially inside and form as an outer contoured shape spring.

According to a further preferred embodiment, one end of the support region merges via an inlet section into the lane change region. The lane change area merges via a discharge section into a beginning of the carrying area. It is advantageous if, in the inlet section, a depth of the rolling element circulation in the radial direction continuously increases from the support region to the lane change region. In the outlet section, a depth of Wälzkörperumlaufs decreases in the radial direction of the lane change area to the support area continuously. In this way, a uniform supply of the rolling elements for and removal of the rolling elements of the lane change region is made possible.

In particular, it is advantageous if the rolling elements are designed as balls. Furthermore, it is advantageous if the Wälzkörperumlauf is designed as a circumferential ball groove. In the support region, the ball groove is preferably formed substantially U-shaped, wherein the balls are immersed in the ball groove substantially with half their diameter in the radial direction of the actuator.

Furthermore, it is advantageous if the depth of the lane change region is substantially equal to, preferably greater than, the diameter of the balls. This means that in the lane change region the balls can dip at least almost completely into the ball channel in the radial direction of the actuating device. The immersion depth must be at least large enough for the balls to be able to change from the track arranged between the first and second turns in the axial direction of the actuating device to the track arranged axially between the second and third turns, without the second winding, in particular the comb of the shaped springs in the region of the second turn to touch. Preferably, the diameter of the balls is smaller than the depth of the lane change area.

The present invention will be explained in more detail below with reference to preferred embodiments in conjunction with the accompanying figures. In these show:

Figure 1 shows an embodiment of an actuating device for a clutch

in a sectional view, 2 shows a Wälzkörpergewindetrieb the actuator of Figure 1 in a side view, and

3 shows a detailed view of a rolling element circulation of the actuating device

from Figure 1 in a support area.

Figures 1 to 3 relate to a preferred embodiment of an actuator 1 for a clutch 2, in particular for a drive train of a motor vehicle.

Features that are not marked in the present description as essential to the invention are to be understood as optional. Therefore, the following description also relates to further embodiments of the actuator 1, the sub-combinations of the features to be explained below. Likewise, the following description relates to the combination or assembly of the actuating device 1 with the clutch 2, in particular in the drive train of a motor vehicle.

The clutch 2 is rotatably mounted about a rotational axis Z and has at least one pressure plate, not shown, at least one counter-pressure plate, not shown, and at least one arranged in the axial direction A of the clutch 2 between the pressure plate and the counter-pressure plate, not shown on the clutch disc. The counter-pressure plate is firmly connected to a housing component of the coupling 2, in particular a clutch cover, in particular screwed. The pressure plate is rotatably mounted in the clutch housing, in particular within the clutch cover and limited in the axial direction A displaced. In particular, the pressure plate is non-rotatably mounted in the clutch housing by means of a plurality of leaf springs, not shown, and biased away from the counter-pressure plate.

In addition, the clutch 2 has a lever element 3, which may be designed as a diaphragm spring for a normally-engaged clutch 2 and for a normally-disengaged clutch 2 as a lever spring. The lever element 3 is supported on the housing side and actuated by the actuating device 1. The housing-side support can be done for example by a coupling plate attached to the bearing unit, not shown, through which the lever member 3 is suspended tilted. For this purpose, the bearing unit has, for example, two wire rings spaced apart in the axial direction A, between which the lever element 3 extends in the radial direction R of the coupling 2. About lever tips, in the radial direction R on the inside of the preferably substantially ring-shaped Hebelele- 3 are arranged, the lever member 3 can be actuated by the actuator 1.

In a normally-engaged clutch 2, the effective force of the trained as a disc spring lever element 3 outweighs the opposing force of the leaf springs, while in a normally extended clutch 2, the opposing force of the leaf springs outweighs the effective force of the lever element formed as a lever spring 3. Accordingly, an operation of the plate spring of the normally-engaged clutch 2 by the actuator 1 for disengaging the clutch 2 by tilting or snapping the plate spring, that is the Abhub the pressure plate and to remove the pressure plate of the platen, while an actuation of the lever spring at a normally-disengaged clutch 2 by the actuator 1 for engaging the clutch 2 by tilting the lever spring leads.

When the clutch 2 is engaged, a torque from the input side of the clutch 2, for example, by a dual mass flywheel, via the clutch housing and both the counter pressure plate and the pressure plate, which are both rotatably connected to the clutch housing, in particular the clutch cover, frictionally transmitted to the clutch disc , From the clutch disc, which is frictionally clamped between the counter-pressure plate and the pressure plate, the torque is transmitted to the output side of the clutch 2, for example to an input shaft of a transmission.

Since due to the frictional engagement both the friction linings of the clutch disc, and to a lesser extent the friction surfaces of the counter-pressure plate and the pressure plate are subject to wear, over the life of the clutch 2, the pressure plate must be moved closer and closer to the platen to the decrease in the thickness of To compensate friction linings and the strength of the friction surfaces in the axial direction A and establish the frictional engagement or to engage the clutch 2 can. For this purpose, a non-illustrated, force-based or path-based wear adjustment device is provided in the clutch 2, for example.

The actuating device 1, which acts on the lever element 3 of the coupling 2, has a stator device 4 and a rotatable rotor device 6 with respect to the stator device 4. For example, the stator 4 may be non-rotatably formed with a support portion, in particular with a housing support. The stator devices preferably form tion 4 and the rotor device 6 an electric motor, in particular a three-phase motor. For this purpose, the stator 4 is provided with a power supply 5 to generate a changing electromagnetic field in not shown, stator-side coils. The rotor device 6 has magnets 7, more specifically permanent magnets, for magnetic interaction with the stator-side electromagnets.

Preferably, the electric motor is designed as a so-called external rotor, that is, the stator 4 is arranged in the radial direction R of the actuator 1 and the clutch 2 within the rotor device 6. However, it is also possible to design the electric motor as an internal rotor, that is, to arrange the stator device 4 in the radial direction R outside the rotor device 6.

The rotor device 6 shown in Figure 1 has a yoke 8auf, on the side of the

Coupling 2, that is, with reference to Figure 1 on the right side, is supported in the radial direction R by a support bearing 9. Thus, in the illustrated embodiment, the support bearing 9 is arranged in the axial direction A of the actuator 1 and the clutch 2 on the opposite side of the power supply 5 for the stator 4. The support bearing 9 can be connected directly or indirectly to the stator 4. The support bearing 9 is preferably designed as a rolling bearing, in particular as a ball bearing, preferably as shown as a double ball bearing. However, a needle bearing or a plain bearing is possible.

In addition to the stator device 4 and the rotor device 6, the actuating device 1 has a relative to the rotor device 6 in the axial direction A limited displaceable carriage device 10. The carriage device 10 is arranged in the radial direction R outside the rotor device 6. The carriage device 10 has an outer sleeve 1 1, which is completed on the side of the power supply 5 for the stator 4, that is, with reference to Figure 1 on the left side, by a cover 12. In the axial direction A between the outer sleeve 1 1 and the cover 12 a shim 13 is arranged to the axial length of the limited by the outer sleeve 1 1 and the lid 12 space for a shaped spring 25 of a Wälzkörpergewindetriebs 22, which will be discussed below to define and adjust. By means of several in the circumferential direction U of the actuator 1 and the clutch 2 arranged screws 14, the cover 12 is screwed through the shim 13 through with the outer sleeve 1 1. In the axial direction A on both sides of the carriage device 10 is in each case one

Kippmomentabstützeinrichtung 15, 16 provided for supporting a force acting on the carriage means 10 tilting moment. Of the two Kippmomentabstützeinrichtungen 15, 16 is a first Kippmomentabstützeinrichtung 15 in the region of a first end of the carriage means 10, with reference to Figure 1 on the left side arranged. A second Kippmomentabstützeinrichtung 16 is disposed in the region of a second, the first end in the axial direction A opposite end, that is, with reference to Figure 1 on the right side of the carriage means 10. The first Kippmomentabstützeinrichtung 15 has a first ring 17 and a first inner sleeve 19th in which, in the illustrated embodiment, an inner periphery of the first ring 17 is in slidable engagement with an outer periphery of the first inner sleeve 19. Similarly, the second Kippmomentabstützeinrichtung 16 has a second ring 18 and a second inner sleeve 20, wherein in the illustrated embodiment, an inner periphery of the second ring 18 is in slidable engagement with an outer periphery of the second inner sleeve 20.

The inner sleeves 19, 20 have a smaller diameter than the outer sleeve 1 1 of the carriage device 10. In particular, both inner sleeves 19, 20 extend in the axial direction A at least partially within the outer sleeve 1 1 of the carriage device 10. The inner sleeves 19, 20 are indirectly or directly attached to the stator 4. The rings 17, 18 are attached directly or indirectly to the carriage device 10. For example, the first ring 17 is pressed into the cover 12 of the carriage device 10, while the second ring 18 is pressed into the outer sleeve 1 1 of the carriage device 10. Preferably, no relative rotational speed occurs between the rings 17, 18 and the corresponding inner sleeves 19, 20 during operation of the actuating device 1, since preferably the carriage device 10 is fixed in terms of rotation with respect to the stator device 4. Thus, preferably, the rings 17, 18 are only in the axial direction A in slidable contact with the corresponding inner sleeves 19, 20th

Each of the two rings 17, 18 has a block-shaped cross-section. Each of the two rings 17, 18 is formed of a rigid material. Alternatively or additionally, each of the two rings 17, 18 is formed of a pressure-stable material.

The two rings 17, 18 are preferably made of a plastic, in particular preferably of polytetrafluoroethylene (PTFE). However, it is also possible that the two rings 17, 18 are formed of a different material, which has a coating with mitigating properties. For example, this coating may be a coating of polytetrafluoroethylene (PTFE). It is also possible that the two rings 17, 18 are formed of a sintered material. It is particularly advantageous if a lubricant is stored in the sintered material.

According to a further, not shown embodiment, it is possible that the first ring 17 with the first inner sleeve 19 is in rollable abutment, while the second ring 18 is located with the second inner sleeve 20 in a rollable system. In particular, the roll-mobile plant may be a plant that can only be moved in the axial direction A. For example, for this purpose, the rings 17, 18 bearings.

The two Kippmomentabstützeinrichtungen 15, 16 opposite in the axial direction A limit a grease space 29, in which a Wälzkörpergewindetrieb 22 associated Wälzkörperumlauf 23, which will be discussed below, is arranged. Preferably, the shaped spring 25 is arranged in the grease space 29. Accordingly, in a particularly preferred embodiment, the two Kippmomentabstützeinrichtungen 15, 16 also assume the functions of seals for sealing the grease chamber 29 to the outside.

In the radial direction R outside the outer sleeve 1 1, a release bearing 21 is provided. The release bearing 21 is formed in the illustrated embodiment as angular contact ball bearings, but may for example be designed as tapered roller bearings, needle roller bearings or plain bearings. About the release bearing 21 and / or the outer sleeve 1 1, the carriage device 10 acts indirectly or directly on the inside in the radial direction R tongues of the lever member 3 to disengage the clutch 2 or einzutücken.

The rolling-element screw drive 22 is preferably arranged in the radial direction R between the rotor device 6 and the carriage device 10. In the illustrated embodiment, the shaped spring 25 of the Wälzkörpergewindetriebs 22 twelve turns, wherein in principle any number of turns greater than / equal to 3 is possible.

In addition to the form spring 25, the Wälzkörpergewindetrieb 22, the already mentioned above Wälzkörperumlauf 23, in which, preferably distributed over the entire circumference, rolling elements 24 in a row, or possibly also in several, in the axial direction A spaced rows are arranged. The Wälzkörperumlauf 23 is in particular trough-shaped or groove-shaped, and may on the one hand be connected as a separate component with the rotor device 6, in particular with the yoke 8, but may also be integrally formed with the rotor device 6 and the yoke 8, as in Figure 1 is shown. In particular, the rolling element circulation 23 is formed in the outer circumference of the rotor device 6 or of the yoke 8, while the drive of the actuating device 1 takes place by means of an external rotor. Conversely, if the drive of the actuating device 1 is effected by means of an internal rotor, it is advantageous if the rolling element circulation 23 is arranged in the inner circumference of the rotor device 6 or of the yoke 8.

The rolling elements 24 run in the grease space 29, which is sealed by the additionally acting as a seal Kippmomentabstützeinrichtungen 15, 16 in the axial direction A, and are preferably formed as balls. However, it is also possible that the rolling elements 24 are formed as needles, or have a barrel or barrel shape. Corresponding to the outer contour of the rolling elements 24, the shaped spring 25 has an abutment contour 27 against which surface regions of the rolling bodies 24 abut. In the illustrated embodiment, the turns of the form spring 25 have two spaced apart in the axial direction A investment contours 27, which are separated by an intervening comb 28 from each other.

The form spring 25 is formed as an inner contoured shape spring 25, since the rolling elements 24 run in the radial direction R within the form of spring 25. Conversely, however, it is also possible that the shaped spring 25 is formed when using an inner rotor as an outer contoured shape spring 25.

The Wälzkörperumlauf 23 has a track change region 30 formed in such a way that the rolling elements 24 in the circumferential direction U before the lane change region 30 in a support portion 31 of the Wälzkörperumlaufs 23 and in the axial direction A between a first and a second turn 26a, 26b of the form spring 25 run, and the rolling elements 24 in the circumferential direction U after the lane change region 30 in the support portion 31 of the Wälzkörperumlaufs 23 and in the axial direction A between the second and a third turn 26b, 26c of the form spring 25 run. Between the first and second turns 26a, 26b of the form spring 25 is thus a first track for the rolling elements 24 defined in the circumferential direction U, while between the second and third turn 26b, 26c of the form spring 25, a second track for the rolling elements 24 in Circumferential direction U is defined. It should be noted at this point that the first winding 26a, the second winding 26b and the third winding 26c represent three successive windings of the shaped spring 25, which may be formed in the axial direction A at any point of the shaped spring 25.

As shown in Figure 2, the second turn 26b crosses over with the

Lane change region 30 when viewing the actuator 1 from the side. The lane change region 30 has a greater depth in the radial direction R than the support region 31. The support region 31 merges into the lane change region 30 via an inlet section 32 and the lane change region 30 merges into the support region 31 via an outlet section 33. The depth of the Wälzkörperumlaufs 23 in the radial direction R increases in the inlet section 32 from the support portion 31 to the lane change region 30 continuously. The depth of the Wälzkörperumlaufs 23 in the radial direction R decreases in the outlet portion 33 of the lane change region 30 to the support portion 31 continuously.

The support portion 31 is formed substantially helically. The pitch of the support portion 31 substantially corresponds to the pitch of the form spring 25 in this area, more specifically the track between the first and second turns 26a, 26b and between the second and third turns 26b, 26c.

The rolling elements 24 are preferably formed as balls. The Wälzkörperumlauf 23 is preferably formed as a circumferential ball groove. In the lane change region 30, it must be ensured that the rolling bodies 24, that is to say the balls, can penetrate under the ridge 28 of the second turn 26b of the shaped spring 25 in the radial direction R, in order to change the lane of one track between the first and second windings 26a. 26b to the other track between the second and third windings 26b, 26c to complete. For this purpose, it is advantageous if the depth of the lane change region 30 is substantially equal to the diameter of the balls. Preferably, the depth of the lane change region 30 is greater than the diameter of the balls, so that they can completely dive into the ball groove and the comb 28 of the second turn 26 b of the form spring 25 certainly not touch.

During operation of the actuating device 1, a rotation of the rotor device 6 by appropriate energization of the stator 4 to a rotation of the Wälzkörperumlaufs 23. The rolling elements 24 pass through the Wälzkörpergewindetriebs 22 the tracks between the first and second winding 26a, 26b of the form spring 25 and between the two - th and third winding 26b, 26c of the form spring 25, whereby the tracks move in the axial direction A, and the rotational movement of the rotor means 6 in a translational movement of the carriage means 10, in which the form spring 25 is mounted axially fixed, is implemented. The translational movement of the carriage device 10 can be used for indirect or immediate operation of the clutch 2.

Since the Wälzkörpergewindetrieb 22 is preferably self-locking, energization of the stator 4 is preferably only necessary if the operating condition of the clutch 2 is to be changed. The energization can be done in both directions of rotation of the rotor device 6, wherein in one direction of rotation, the clutch 2 is engaged, and in the opposite direction of rotation, the clutch 2 is disengaged. In a co-rotating stator 4, however, other types of energization are possible.

The preceding embodiments relate to an actuating device 1 for a clutch 2 with a stator 4, a relative to the stator 4 rotatable rotor means 6 and a relative to the rotor device 6 in the axial direction A limited displaceable carriage means 10, wherein between the rotor means 6 and the carriage means 10 a Wälzkörpergewindetrieb 22 is provided with at least three windings 26a, 26b, 26c and a Wälzkörperumlauf 23 with rolling elements 24, wherein the Wälzkörperumlauf 23 has a track change region 30 formed such that rolling elements 24 in the circumferential direction U before the lane change region 30 between a first and a second turn 26a, Run 26b, and rolling elements 24 in the circumferential direction U after the lane change region 30 between the second and a third turn 26b, 26c run, wherein at least one Kippmomentabstützeinrichtung 15, 16 for supporting a on the carriage direction 10 acting tilting moment is provided.

List of Reference Actuator

clutch

lever member

stator

power

rotor means

magnet

yoke

support bearings

carriage means

outer sleeve

cover

shim

screw

first Kippmomentabstützeinrichtung

second Kippmomentabstützeinrichtung

first ring

second ring

first inner sleeve

second inner sleeve

release bearing

rolling bodies

roller system

rolling elements

shaped spring

a first turn

b second turn

c third turn

contact contour

Comb

grease chamber

Lane change area 31 support area

32 inlet section

33 outlet section A axial direction R radial direction U circumferential direction Z axis of rotation

Claims

claims

1 . Actuating device (1) for a clutch (2) with a stator device (4), a rotatable rotor device (6) with respect to the stator device (4) and a carriage device (10) displaceable in the axial direction (A) relative to the rotor device (6), wherein between the rotor means (6) and the carriage means (10) is provided a Wälzkörpergewindetrieb (22) with at least three windings (26a, 26b, 26c) and a Wälzkörperumlauf (23) with rolling elements (24), wherein the Wälzkörperumlauf (23) a in such a way formed lane change region (30) that rolling elements (24) in the circumferential direction (U) before the lane change region (30) between a first and a second turn (26a, 26b) run, and rolling elements (24) in the circumferential direction (U) after the Spurwechselbereich (30) between the second and a third turn (26b, 26c) run, wherein at least one Kippmomentabstützeinrichtung (15, 16) for supporting a on the Schlitteneinrichtu ng (10) acting tilting moment is provided.

2. Actuating device (1) according to claim 1, wherein a first Kippmomentabstützeinrichtung (15) in the region of a first end of the carriage means (10) is arranged, and wherein a second Kippmomentabstützeinrichtung (16) in the region of a second, the first end in the axial direction ( A) opposite end of the carriage device (10) is arranged.

3. Actuating device (1) according to claim 1 or 2, wherein two in the axial direction (A) opposite Kippmomentabstützeinrichtungen (15, 16) define a grease space (29), in which the Wälzkörperumlauf (23), and preferably a form spring (25), at least the first, second and third winding (26a, 26b, 26c), is / are arranged.

4. Actuating device (1) according to at least one of claims 1 to 3, wherein the Kippmomentabstützeinrichtung (15, 16) at least one ring (17, 18) and at least one inner sleeve (19, 20), and wherein the ring (17, 18) in slidable or roll-movable contact with the inner sleeve (19, 20).

5. Actuator (1) according to claim 4, wherein the ring (17, 18) is attached directly or indirectly to the carriage means (10), and wherein the inner sleeve (19, 20) is attached directly or indirectly to the stator means (4) ,

6. Actuator (1) according to claim 4 or 5, wherein the inner sleeve (19, 20) has a smaller diameter than an outer sleeve (1 1) of the carriage device (10).

7. Actuating device (1) according to at least one of claims 4 to 6, wherein the ring (17, 18) has a block-shaped cross section, and is preferably formed of a rigid and / or pressure-resistant material.

8. Actuating device (1) according to at least one of claims 4 to 7, wherein the ring (17, 18) made of a plastic, preferably made of polytetrafluoroethylene (PTFE), or a sintered material, preferably with a stored lubricant is formed.

9. Actuator (1) according to at least one of claims 4 to 8, wherein the ring (17, 18) has a coating with friction-reducing properties, preferably of polytetrafluoroethylene (PTFE).

10. Actuating device (1) according to at least one of claims 4 to 6, wherein the ring (17, 18) has a rolling bearing.